US6149384A - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

Info

Publication number
US6149384A
US6149384A US09/066,913 US6691398A US6149384A US 6149384 A US6149384 A US 6149384A US 6691398 A US6691398 A US 6691398A US 6149384 A US6149384 A US 6149384A
Authority
US
United States
Prior art keywords
centrifugal pump
rotor
pump according
casing
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US09/066,913
Other languages
English (en)
Inventor
Vaclav Feres
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US6149384A publication Critical patent/US6149384A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/12—Pumps with scoops or like paring members protruding in the fluid circulating in a bowl

Definitions

  • the present invention relates to a centrifugal pump.
  • a pump disclosed in U. S. Pat. No. 4,171,182 operates with which liquid being discharged from an underpressure or vacuum chamber.
  • a rotor rotates in a tight casing and has several delivery ducts extending outwards from the center and to whose outlet is in each case connected a short, siphon-like deflection or return with an overflow.
  • the liquid supplied in the center of the rotor is centrifugally accelerated into the delivery ducts and inwardly deflected at the outlet thereof.
  • the liquid runs out into the casing and is tangentially discharged from the latter.
  • the rotor By means of a centrally introduced line, the rotor is connected to the vacuum chamber, so that there is a pressure compensation between the vacuum chamber and the low pressure side of the pump. Sealing between the interior of the rotor and the pressure side takes place by the siphon-like deflection, in much the same way as in a liquid seal pump.
  • the invention provides a centrifugal pump which operates to discharge liquids from process equipment with vacuum and, as a result, the aforementioned disadvantages do not arise.
  • the centrifugal pump of the invention operates so that for discharging the liquid from a vacuum chamber, a gas phase in the discharge chamber is linked by means of an open line introduced into the latter with the gas phase of the vacuum chamber and that the scoop pipe is closed on the outlet side by an automatically closing check valve, which opens under the operating pressure.
  • the pump operates in the low pressure range against atmospheric pressure or the delivery head of the following process stage.
  • the valve located at the outlet or drain side ensures that the vacuum in the pump and process device is maintained if the scoop pipe delivers no liquid or the pump is stationary. During operation the valve only opens if the liquid discharged by the scoop pipe has a pressure, which is at least slightly above the counterpressure.
  • the pump constructed according to the invention is suitable for use in random, process engineering plants, where processes take place under vacuum and there is a need for drawing liquids out of the process.
  • the inventive pump Compared with positive displacement pumps, the inventive pump has the advantage that the liquid can also contain solid particles, without damage occurring on the rotating parts of the pump. It is also possible to deliver viscous, foaming or boiling liquids. With a constant rotation, the pump delivers without any control member, even in the case of feed quantities fluctuating between zero and a maximum value.
  • the connecting line between the gas phase of the process device and the discharge chamber issues into the discharge chamber in the area of the rotor axis.
  • the thickness of the liquid ring can vary within certain limits on the inner circumference of the discharge chamber without impairing the function of the pump.
  • the thickness of the liquid ring for a constant feed height and constant speed of the rotor, is obtained as a function of the counterpressure at the check valve.
  • the line advantageously has a gradient, in order to divert into the pump the condensate produced in a vapor phase in the vacuum chamber.
  • the scoop pipe On the pressure side the scoop pipe is preferably sealed by a disk check valve, which opens against the counterpressure under the operating pressure of the pump.
  • slip ring seal in the casing.
  • the slip ring seal which can be constructed both axially and radially, is immersed in a lubricating sealing liquid located within the closed chamber of the casing. This ensures that the pump can also be operated “dry", i.e. without any delivery liquid supply.
  • the sealing liquid As liquids in process equipment, e.g. vacuum evaporators, frequently have high temperatures, the sealing liquid also fulfils a cooling function, which in particular protects the slip ring seal against undesired heating.
  • the rotor is mounted by means of the slip ring seal in the casing.
  • the slip ring seal seals the feed side of the rotor against the casing, which ensures that the casing remains free from delivery fluid.
  • the casing has at least two areas, which are sealed against one another by means of the slip ring seal located on the rotor drive shaft and the casing area receiving the rotor is connected to the rotor interior and is sealed in liquid-tight manner against the same by a rotating, contact-free gap seal or gland.
  • the gland according to this variant has ribs with axial holes and chambers enclosed by them, so that spray penetrating the gland from the rotor can be returned to the latter as a result of the rotary movement of the gland.
  • the tangential connection is connected by means of a check valve to the pump feed.
  • the sealing liquid travels in a closed circuit with a feed and drain on the pump casing, which carries the sealing liquid through a cooling device located within the pump casing and preferably a spiral cooler or radiator concentrically surrounding the chamber.
  • the conveying of the sealing liquid in the circuit takes place by means of a pump rotor, which is located in the closed chamber and rotates with the rotor.
  • the pump rotor has, in a preferred development, drivers for the slip rings of the slip ring seal.
  • the part of the sealing liquid circuit outside the pump casing advantageously has a filter and a level indicator, which is used for checking the sealing liquid during operation and on topping up the liquid.
  • the pump can be constructed with a radially positioned slip ring seal and a correspondingly shorter, axial overall length.
  • a detachable attachment or fixture is placed on the feed-side cover of the pump casing. It has a holding pipe directed into the pump interior and on which the scoop pipe is positioned in non-rotary manner and detachably fixed. After releasing the attachment, the holding pipe and scoop pipe can be removed from the rotor and the scoop pipe can be removed from the holding pipe for replacement purposes or for cleaning in the case of blockages.
  • the pump according to the invention must also be suitable for the discharge of very hot and optionally also boiling process liquids, e.g. from a fine vacuum evaporator, on its drive side the rotor has an air-cooled hub for connection to the drive shaft.
  • FIG. 1 A longitudinal section through the centrifugal pump with an axial construction of the slip ring seal.
  • FIG. 2 A longitudinal section through the centrifugal pump with a radial construction of the slip ring seal.
  • FIG. 3 A view of the pump rotor in the sealing liquid circuit.
  • FIG. 4 A section IV--IV according to FIG. 3.
  • FIG. 5 A cross-section through the sleeve receiving the chamber with the sealing liquid.
  • FIG. 6 A longitudinal section through the centrifugal pump according to an alternative embodiment.
  • the centrifugal pump has a casing 1 with a substantially cylindrical cross-section, which at each of its ends is closed by a cover 2, 3.
  • a partition 60 which subdivides the casing interior into an area, where the rotor runs under ambient conditions, and a second area sealed with respect to the first area and the environment, in which are inter alia located the devices for sealing the vacuum area of the pump.
  • the rotor 4 has on its one end face a hub 5 for the connection of the drive shaft 6, which is mounted in a frontal termination 7 of the casing 1.
  • the rotor 4 has on the end face facing the drive shaft 6 a central opening 8, which in the embodiment according to FIG.
  • the rotor 4 is connected to a feed 10 by means of which the pump is connected to the liquid outlet of a process plant 10', e.g. a vacuum evaporator.
  • a process plant 10' e.g. a vacuum evaporator.
  • the liquid to be discharged from the process plant passes by means of the feed 10 to the pump.
  • the rotor 4 On the feed side and connecting on to the opening 8, the rotor 4 has a feed chamber 11, which is separated from the remaining rotor by a partition 12. Between the partition 12 and the closed end wall 13 of the rotor 4 can be inserted several webs 14, which act as radial blades. On the other side of the partition 12 the rotor 2 forms a discharge chamber 15. The partition 12 does not extend completely up to the circumferential wall 16 of the rotor 4, so that a free overflow ring 17 remains, by means of which the discharge chamber 15 is connected to the feed chamber 11.
  • a line 19 which passes outwards through the hollow shaft 9 and through the front cover 3 of the casing 1.
  • This line 19 is tightly connected with the gas phase of the process plant under vacuum and towards the pump has a gradient.
  • the line 19 passes substantially centrally through the partition 12.
  • a scoop pipe 20 Through the hollow shaft 9 and opening 8 is also passed into the rotor 4 a scoop pipe 20 and it passes through the partition 12 and is bent outwards in the discharge chamber in such a way that at its feed end 21 it is oriented against the rotation direction of the rotor, e.g. runs roughly parallel to the circumferential wall 16 of rotor 4.
  • a screwed pipe coupling 23 At its other end, with which the scoop pipe is roughly in the axis of the rotor 4, it is detachably fixed by a screwed pipe coupling 23 to a holding pipe 24, which is in turn part of an attachment or fixture 25, which is detachably fixed to the front cover 3 of the casing 1 and enclosed the feed 10.
  • the pump outlet or drain 26 On the attachment 25 is also located the pump outlet or drain 26, which has a closure member in the form of a disk check valve 27 with a valve disk 29 loaded by a spring 28.
  • the check valve hermetically seals the rotor against the environment, so that by means of the pump drain 26 there can be no inrush of air into the process plant.
  • the rotor 4 is sealed in the casing 1 by means of a slip ring seal 30, which in the construction according to FIG. 1 is in the form of an axial double slip ring seal, which is positioned between the cover 3 and the dividing wall 60 of the casing 1. It has two slip rings 31, 32 positioned in spaced manner on the hollow shaft 9 of the rotor 2 and in each case outwardly displace counterrings 33, 34, the rings 31, 33 and 32, 34 forming on their facing, lapped end faces the sealing faces and for this purpose are under the action of not shown compression springs.
  • the rings 31 to 34 are concentrically surrounded by a split sleeve 35, 35a, whose two parts are fixed in the casing 1.
  • the chamber 36 formed between the slip rings 31 to 34 and the sleeve 35, 35a receives a lubricating sealing liquid which, in the represented embodiment, simultaneously serves as a coolant.
  • a further chamber 37 containing a spiral cooler or radiator 38, through which flows a heat exchange fluid, is arranged concentrically to the chamber 36.
  • a pump rotor 39 which is connected in non-rotary manner by a spring clip 40 to the hollow shaft 9 of the rotor 4 and is guided on its circumference in an annular groove of the sleeve 35.
  • driving pins 41 On the pump rotor 39 are located driving pins 41, which engage on and drive the inner slip rings 31, 32.
  • the pump rotor has three driving pins 41, which are firmly seated in coaxial holes or bores.
  • the pump rotor also has several coaxial holes 42, to which is in each case connected a radial hole 43.
  • the sealing liquid in the chamber 36 is fed by means of the coaxial holes 42 and centrifugally accelerated in the radial holes 43.
  • To the sleeve 35 is tangentially connected a discharge pipe 44 (FIG. 5), through which the sealing liquid accelerated by the pump rotor is discharged in a circuit 45 (FIG. 1), in which are located a filter 46 and a level indicator 47, e.g. in the form of a sight glass.
  • the sealing liquid passes via feed 48 back into the casing 1, namely into the outer chamber 37 with the spiral cooler 38 and from there, via the holes 49, back into the inner chamber 36 with the slip rings 31 to 34.
  • the liquid to be discharged is supplied to the pump by means of the feed 10 and hollow shaft 9.
  • the liquid entering the feed chamber 11 of the rotor 4 by means of the opening 8 is centrifugally accelerated and passes via the overflow ring 17 into the discharge chamber 15, where it is spread in ring-like manner on the inside of the circumferential wall 16 of the rotor 4.
  • the scoop pipe 20 immersed with the feed end 21 in the liquid ring removes liquid from the ring and converts the kinetic and static energy of the liquid into pressure energy.
  • the liquid scooped from the feed end 21 passes through the scoope pipe and holding pipe 24 to the check valve 27 which, under the operating pressure, opens the pump, so that the liquid is discharged via the drain 26.
  • the sealing liquid of the slip ring seal 30 is constantly circulated, filtered and cooled by means of the pump rotor 39, which is driven by the rotor 4. Therefore the pump can also run "dry”, i.e. without any liquid supply and even under elevated temperature in the pump chamber. Therefore the pump has good antiseizure properties.
  • the check valve 27 closes, so that the vacuum from the process plant prevailing in the rotor is maintained.
  • FIG. 2 differs from that according to FIG. 1 essentially only with respect to the sealing of the rotor. Therefore for the same parts the same reference numerals are used and with respect to these parts reference is made to the description of FIG. 1.
  • the rotor 4 has no hollow shaft and the slip ring seal 30 is constructed as a double radial seal. It comprises a slip ring 50 tightly inserted in the rotor opening 8 and which cooperates by means of two concentric ring faces with two concentric counterrings 51, 51a in the casing 1.
  • the counterrings 51, 51a are placed between an inner sleeve 52 and an outer sleeve 53 of the casing, accompanied by the interposing of two concentric O-rings 54, 54a and are forced by means of two spring-loaded, concentric thrust rings 56, 56a against the slip ring 50.
  • the slip ring seal is connected to a chamber 57, which once again contains a lubricating and cooling sealing liquid.
  • the operation of the pump is the same as described relative to FIG. 1. Diverging therefrom, the lubricating sealing liquid is not circulated with its own pump (not shown in FIG. 1).
  • the hub 5 of the rotor 4 serving to connect the drive shaft 6 is provided with a ribbed radiator or cooler 59, which rotates with the hub in a space open to the environment between the front cover 2 of the casing and the termination 7, together with the main bearing.
  • the ribbed radiator 59 gives off the heat to the ambient air in the chamber 58.
  • FIG. 6 shows an alternative embodiment of the scoop pipe pump, the same parts having the same reference numerals as in the preceding drawings and only the differences compared with the preceding embodiment will be described hereinafter.
  • an area 61 of the casing 1 is connected to the discharge chamber 15 of the rotor 4 and is sealed in liquid-tight, but not gas-tight manner with respect thereto by a gland 62.
  • the gland rotating with the rotor 4 and contact-free with respect to the hollow shaft 9, has ribs 63, which enclose gaps, each rib having at least one axial hole 64.
  • spray entering the gland in the rotor is fed back into the latter through the rotary movement of the gland.
  • the casing area 61 connected to the rotor interior is, according to the embodiment shown in FIG. 6, sealed against the atmosphere by means of an axial double slip ring seal 30, constructed in accordance with the slip ring seal described in FIG. 1 and located on the drive shaft 6 of the rotor 4.
  • an axial double slip ring seal 30 constructed in accordance with the slip ring seal described in FIG. 1 and located on the drive shaft 6 of the rotor 4.
  • the chamber 36 for receiving the lubricating sealing liquid, the chamber 36 is only constructed with one feed and removal connection 67. There is no need for a circuit guidance with cooling for the sealing or lubricating liquid, because the slip ring seal according to the variant of FIG. 6 does not come into contact with possibly hot and/or aggressive delivery liquid.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Centrifugal Separators (AREA)
US09/066,913 1997-03-01 1998-04-28 Centrifugal pump Expired - Fee Related US6149384A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19718283 1997-03-01
DE19718283A DE19718283C1 (de) 1997-05-01 1997-05-01 Zentrifugalpumpe

Publications (1)

Publication Number Publication Date
US6149384A true US6149384A (en) 2000-11-21

Family

ID=7828232

Family Applications (1)

Application Number Title Priority Date Filing Date
US09/066,913 Expired - Fee Related US6149384A (en) 1997-03-01 1998-04-28 Centrifugal pump

Country Status (6)

Country Link
US (1) US6149384A (cs)
JP (1) JP2966831B2 (cs)
CH (1) CH692753A5 (cs)
CZ (1) CZ286478B6 (cs)
DE (1) DE19718283C1 (cs)
SE (1) SE515519C2 (cs)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110180151A1 (en) * 2008-06-25 2011-07-28 Basf Se Method for safely preventing backflowing in the conveying of a fluid
US20190249939A1 (en) * 2018-02-14 2019-08-15 Nidec Sankyo Corporation Cooling device

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999882A (en) * 1975-03-17 1976-12-28 Dresser Industries, Inc. Flushing and cooling system for shaft seals and pumps
US4036427A (en) * 1975-06-06 1977-07-19 Kobe, Inc. Combination pitot pump and centrifugal separator
US4044943A (en) * 1976-06-21 1977-08-30 Kobe, Inc. Centrifugal separator and system
US4183713A (en) * 1975-11-17 1980-01-15 Kobe, Inc. Pitot pump with jet pump operated thrust balance
US4279571A (en) * 1979-10-01 1981-07-21 Kobe, Inc. Pitot pump with fluid lubricated bearings
US4946349A (en) * 1989-07-19 1990-08-07 National Space Development Agency Of Japan Water ring vacuum pump

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE972631C (de) * 1953-05-21 1959-08-20 Westfalia Separator Ag Verfahren und Vorrichtung zur Reinigung von schweren Heizoelen
US3049081A (en) * 1959-04-27 1962-08-14 Bell Aerospace Corp Pump seal
US3795459A (en) * 1973-03-21 1974-03-05 Kobe Inc Pitot pump with slotted inlet passages in rotor case
US4171182A (en) * 1978-05-08 1979-10-16 Vaclav Feres Extractor pump for fluids under vacuum

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999882A (en) * 1975-03-17 1976-12-28 Dresser Industries, Inc. Flushing and cooling system for shaft seals and pumps
US4036427A (en) * 1975-06-06 1977-07-19 Kobe, Inc. Combination pitot pump and centrifugal separator
US4183713A (en) * 1975-11-17 1980-01-15 Kobe, Inc. Pitot pump with jet pump operated thrust balance
US4044943A (en) * 1976-06-21 1977-08-30 Kobe, Inc. Centrifugal separator and system
US4279571A (en) * 1979-10-01 1981-07-21 Kobe, Inc. Pitot pump with fluid lubricated bearings
US4946349A (en) * 1989-07-19 1990-08-07 National Space Development Agency Of Japan Water ring vacuum pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110180151A1 (en) * 2008-06-25 2011-07-28 Basf Se Method for safely preventing backflowing in the conveying of a fluid
US9086191B2 (en) * 2008-06-25 2015-07-21 Basf Se Method for safely preventing backflowing in the conveying of a fluid
US20190249939A1 (en) * 2018-02-14 2019-08-15 Nidec Sankyo Corporation Cooling device
US11085711B2 (en) * 2018-02-14 2021-08-10 Nidec Sankyo Corporation Cooling device

Also Published As

Publication number Publication date
CZ134198A3 (cs) 1999-06-16
SE515519C2 (sv) 2001-08-20
SE9801449L (sv) 1998-11-02
SE9801449D0 (sv) 1998-04-24
DE19718283C1 (de) 1998-11-19
JPH10318177A (ja) 1998-12-02
JP2966831B2 (ja) 1999-10-25
CZ286478B6 (en) 2000-04-12
CH692753A5 (de) 2002-10-15

Similar Documents

Publication Publication Date Title
US5009578A (en) Motor driven pumps
US2575568A (en) Centrifugal gas-liquid separator
US4389052A (en) Oil seal system for shaft of turbocharger
US5727792A (en) Triple cartridge seal having one inboard and two concentric seals for chemical processing pump
US2319730A (en) Pump
US5525039A (en) Hermetically sealed magnetic drive pump
US3816020A (en) Pump
US2886350A (en) Centrifugal seals
RU2662845C2 (ru) Проточный насос с трубками пито с зубчатым приводом
US6131914A (en) Gas turbine engine bearing compartment seal
US2005429A (en) Centrifugal pump and the like
US2741991A (en) Pump and packing
US6149384A (en) Centrifugal pump
US3856430A (en) Diffuser with boundary layer removal
US2684034A (en) Liquid cooling structure for pump shafts
US5911565A (en) Pump for conveying hot media
JPS614897A (ja) 軸流フアンの回転する軸受けを潤滑し、かつ冷却する方法、並びにこの方法を実施するための軸流フアン
US2390332A (en) Blower apparatus
US3838939A (en) Pitot pump with means for excluding leakage from bearings
US2766698A (en) Pump
US2340747A (en) Method and apparatus for pumping volatile liquids with rotary elements
US3795457A (en) Multistage pitot pump with means for feeding clean fluid to seals
US2775208A (en) Rotary pumps
US4342537A (en) Impeller pump and seal
US1942139A (en) Molecular vacuum pump

Legal Events

Date Code Title Description
FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: SMALL ENTITY

FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20121121